Vibration-resistant low NOx burner

Abstract: A low NO x burner (2) includes a primary air and fuel discharge assembly which, in turn, includes a burner plate (6) having a plurality of slots (32) from which fuel gas jets and combustion air are discharged. The slots are arranged such that the width of the recirculation zones between adjacent slots substantially varies between the central region of the burner plate and its perimeter. With this construction, the local ignition patterns vary such that local oscillations of flame front occur at different frequencies so that vibrations are greatly dampened and resonance problems in the furnace minimized or eliminated. In applications where high excess air is not desirable, such as boiler applications, the burner is modified by providing a secondary fuel and flue gas injection assembly (80) to form a two stage burner (2'). In the preferred embodiment, the secondary injection assembly includes a plurality of discrete fuel and flue gas injection tubes (82, 94) arranged around the primary air and fuel gas discharge assembly (50). The secondary fuel and flue gases are directed radially inward and downstream from the burner plate so that they mix with the combustion air entering through the burner plate slots (32) in a secondary combustion zone. The resulting delay in the combustion of the secondary fuel gas and the need for heating the flue gas lowers the overall combustion temperature, which in turn reduces the NO x formation in the second or downstream combustion zone.

Description: BACKGROUND OF THE INVENTION The present invention relates to burners generally, and more particularly to a low NO x burner having enhanced flame stability and a construction that minimizes vibration generation and accompanying furnace rumble (low-frequency loud noise). Generally, NO x emissions rise exponentially with combustion temperature. These emissions typically are reduced by lowering combustion temperatures. In some cases this is accomplished by combusting the fuel with an increased amount of excess air (lean mixture). One example of a system using excess air to reduce NO x emissions is disclosed in the article "The Development of a Natural Gas-Fired Combustor for Direct-Air" from the 1992 International Gas Research Conference. In this burner system, the fuel and gas are premixed and then injected in the combustion chamber. The air-fuel mixture is adjusted to provide whatever amount of excess air is desired to lower the temperature so that NO x emissions are minimized. However, one of the drawbacks of this system is that there remains the danger of explosions upstream from the combustion chamber, for example, in the burner. In U.S. Patent No. 5,102,329, a low NO x burner is disclosed, in which mixing of fuel gas and combustion air to the extent necessary for combustion in the burner is precluded. In this burner, fuel tubes or spuds are arranged over slots in a burner plate to discharge fuel gas therethrough at high velocities. Combustion air also is discharged from the burner through these slots. Although some mixing of fuel gas and combustion air (controlled exclusively by fuel gas jet entrainment of the combustion air) occurs along the boundary line between each cone-shaped fuel gas jet and the air, the space volume where this mixing occurs is negligible. In addition, the flow pattern in this area has a velocity component in the downstream direction that many times exceeds the propagation velocity of the flame. Accordingly, any flame flashback from the combustion chamber is precluded. Although the above systems advantageously reduce NO x emissions, and in the latter case, minimize the possibility of flame flashback, they are subject to combustion or air flow driven pulsation of the flame front, which causes strong vibration and rumbling in the furnace. In burners generally, the combustion amplifies pulsations which typically occur at a frequency of about 8-200 Hz due to the particular characteristics of the air supply fan or duct work, for example, or resonance modes of a furnace. It has been found that when heat of combustion is applied rapidly and uniformly to the flow of fuel and air downstream of the burner in the area of combustion, these pulsations can be amplified more easily. As a result, the flame front oscillates toward and away from the burner plate at a frequency determined by the system. This leads to vibrations, and causes resonance of the hardware of the furnace, known as rumbling. These vibrations, and resonance problems are of particular concern in large combustion devices. Another way to reduce flame temperature, and consequently NO x emissions, is to enhance entrainment of relatively cold oxygen deficient gases from the furnace volume into the combustion space by using the kinetic energy of the air and fuel flows. One example of this is the "transjet" burner manufactured by Hague International. The drawbacks of this design are its inability to effectively control NO x emissions with an increase of excess air, large size for a given heat input, and high air pressure requirement. Expensive heat and corrosion resistant materials also are required with this system. US-A-1,643,788 discloses a combination oil and gas burner whereby either gaseous or liquid combustibles may be efficiently burned without overheating of the parts and has for its object to provide a device which will permit the change from one fuel to another in a minimum of time, as well as a use of both gaseous and liquid combustibles simultaneously during the period of change. Further, to prevent overheating and distortion of parts, a further object is to provide a means of supplying a cooling medium to the heated parts through the gas chamber while burning oil and through the air register while burning gaseous fuel. This pre-known burner comprises a burner plate having an outer surface for facing a combustion chamber, an inner surface, and a plurality of circumferentially arranged generally radially extending slots formed therethrough for introducing air and fuel gas into a combustion chamber; and a plurality of circumferentially arranged generally radially extending burner tubes each having an inner end portion adapted to be coupled to a fuel gas source and an outer end portion, each tube including a plurality of discharge openings and being oriented such that its discharge openings are aligned with one of said slots for directing fuel gas therethrough. The burner plate has the shape of a conical diffuser with openings and extensions, and to discharge gas through any other one of the closed spaced openings and the corresponding extensions gas pipes are provided for only each second opening. This diffuser acts as a partial shield to an oil spray injected with an atomizer so that the air for combustion will not strike the spray with full force. However, this documents is silent on the problems to produce a flame with enhanced stability to dampening of vibrations, minimizing or elimination of resonance problems and further reduction of NO x emissions. SUMMARY OF THE INVENTION The present invention is directed to a burner which avoids the problems and disadvantages of the prior art. This goal is accomplished by providing a burner construction according to claim 1 in which local oscillations of flame fronts are generated in the combustion chamber downstream from the burner at different frequencies which are not synchronized. In this way, vibrations are greatly dampened and resonance problems are minimized or eliminated. At the same time the burner construction is also advantageous for further reduction of NO x emissions by rapid entrainment of gases from the furnace volume into the combustion region. According to the present invention, a burner is provided with an annular burner plate having a plurality of slots for introducing air and fuel gas into a combustion chamber. The slots are arranged such that the recirculation zone area between adjacent slots substantially varies between the burner center and perimeter. For example, the slots are arranged such that the distance between adjacent slots substantially varies between the central portion of the burner plate and the burner plate perimeter (i.e., they are nonparallel). The slots can be arranged in numerous configurations such as a triangle or in a star configuration where the slots are generally radially arranged. In the preferred embodiment the burner slots are generally radially arranged with their inner-end portions adjacent the center portion of the burner plate. A plurality of generally radially arranged burner tubes or spuds, each having an outer end portion and an inner end portion, are spaced from the slots and aligned therewith. Each burner tube includes a plurality of discharge openings aligned with one of the slots for directing fuel gas therethrough. The slots are oriented such that the distance between the outer end portions of adjacent slots is substantially greater than the distance between the inner end portions of those adjacent slots. It follows that the distance between the outer end portions of adjacent burner tubes also is substantially greater than the distance between the inner end portions of those adjacent tubes. Preferably, the ratio between the distance between the outer end portions and the distance between the inner end portions is at least about 2:1. The combustion occurs at a point downstream from the burner plate where the fuel gas is mixed with enough excess air to prevent the combustion temperature from becoming too high, thereby limiting NO x production. This is done by a combination of steps: preventing an immediate ignition of the gas as it exits from the burner tubes by enveloping the gas with air along the distance from the spuds to the slots, and then inducing turbulence. Turbulence is created by discharging the gas and air at high speeds. As the gas and air emerge from the burner plate the discharged air and gas slow down. The resulting energy loss is converted into desirable turbulence. As the gas stream travels downstream, it expands in a cone shape and increasingly mixes with air and with recirculating hot gases. Under these conditions, ignition starts from the periphery of the cone shaped jets discharging from the burner plate slots, where fuel gas concentration is close to the lean flammability limit, and propagates by turbulent mixing of the recombustion gases to the jet centers. Thus, local fuel-air ratios during combustion do not exceed the average, based on total fuel and air input to the burner, and NO x formation is thereby diminished. As a result of the burner tube and slot arrangement, the width of the recirculating air zones between slots varies significantly in the radial direction. Thus, the recirculating areas of hot combustion products in the wake of the plates between slots varies significantly in the radial direction, so that local ignition patterns also vary. As a result, local oscillations of flame fronts tend to occur at different frequencies and are not synchronized. In this way, vibrations are greatly dampened and resonance problems are minimized or eliminated. Preferably, a central gas nozzle is provided so that a more complex flame front shape is generated, which further reduces the possibility of undesirable vibration and provides enhanced flame stability. In one example, which has provided the desired results, the gas nozzle is arranged at the center of the burner plate and is provided with fuel gas discharge ports oriented to direct fuel gas in a direction tangential to the nozzle so as to induce gas exiting therefrom to swirl downstream from the burner plate. A spinner also can be arranged around the central gas nozzle to cause combustion air channeled around the central gas nozzle to swirl downstream from the nozzle. With this arrangement, flame stability without air preheat is achieved with up to 110% excess air for natural gas firing. With the above design, the burner is more stable even when equipped with a very short throat. A typical throat length might be 30% of the burner diameter. As the flow of partially burned fuel and air is exiting the throat it has a spoky or star shaped pattern of flat jets. This flow entrains gases from the furnace volume more rapidly than the flow exiting a conventional burner. Thus, the flow of fresh hot combustion products becomes rapidly quenched, and NO x formation minimized. The foregoing burner configurations, together with the large amount of excess combustion air, i.e., more than stoichiometric, supplied through the burner plate slots, keeps the flame relatively cool to minimize the generation of NO x . Although excess air burners are useful for duct heaters, they are generally relatively inefficient for heating furnaces, boilers and the like. For the latter applications, the burner discussed above is modified by providing a secondary fuel gas and flue gas injection assembly to form a two-stage burner assembly. According to this embodiment of the invention, a burner assembly including a primary air and fuel gas discharge assembly, such as a burner tube and slot arrangement as discussed above, for discharging a mixture of primary fuel gas and air into a combustion chamber, is provided with a plurality of discrete secondary fuel gas injection tubes and forced recirculation flue gas injection tubes, both arranged around the primary air and fuel gas discharge assembly. Each injection tube has a discharge end portion that is radially spaced from the primary air and fuel gas discharge assembly. The secondary fuel gas injection tubes include an inlet portion adapted for coupling to a secondary fuel gas source, while the flue gas injection tubes include an inlet portion adapted for coupling to a flue gas recirculation line. During operation of the two-stage burner assembly, the flue gases generated in the combustion chamber flow to a flue gas stack where a portion of those gases are drawn into a recirculation line including a fan which feeds into the flue gas injection tubes. The secondary fuel gas together with the recirculated flue gas, are then injected under pressure into the combustion flame at a particular region of the flame. Since the recirculated flue gases, as well as the secondary fuel gas, are discharged in a forced draft, the direction of the flue and fuel gas jets or streams discharged from the flue gas and secondary fuel gas tubes can be controlled to reach the combustion flame at the desired location. In this manner, two combustion zones can be generated in the combustion chamber such that NO x formation is minimized and a relatively high heat capacity maintained when low excess air burner input is required as discussed in more detail below. When using 15% excess air (e.g., about 3% in excess of stoichiometric concentration of oxygen) with the primary air and fuel gas discharge assembly, some of the air is not consumed in the first upstream combustion zone where lean combustion takes place, while the excess air keeps to flame temperature relatively low. By angling the recirculation flue gases and secondary fuel gas toward the centerline of the burner plate, they mix with the combustion air entering through the burner plate slots so that the fuel gas from the secondary nozzles combusts some distance downstream of the burner plate, i.e., in a secondary combustion zone. The excess of air in the first zone acts as a diluent which lowers the temperature of the burning gases and thereby reduces NO x formation in the first zone. However, since the secondary fuel gas is not supplied with air, but, instead with the recirculated flue gas (which contains very little, e.g., 3%, oxygen), combustion is delayed and the volume of nonreacting gases downstream of the burner is increased. The resulting delay in the combustion of the secondary fuel gas and the need for heating the flue gas lowers the overall combustion temperature, which in turn reduces the NO x formation in the second or downstream combustion zone. The two-stage burner assembly also advantageously operates with relatively low temperature recirculation flue gases without the need for cooling surfaces inside the furnace. First, flue gases are drawn from the flue gas stack where flue gas temperatures are relatively low, e.g., about 300°F. In addition, the flue gases are routed external to the combustion chamber, thereby allowing further cooling before being recirculated into the combustion chamber via the flue gas injection tubes. The relatively cool recirculation flue gases eliminate the need to rely on internal furnace surfaces for cooling the flue gas to the desired temperature. This is especially important when such cooling surfaces are not readily available such as in boiler installations. While the single stage burner described above can achieve an excellent 80% reduction in NO x formation, the addition of the secondary fuel gas discharge assembly (including recirculation flue gas and secondary fuel gas injection tubes) has been found to produce up to 95% reduction in NO x formation. The two-stage burner assembly also is of relatively simple construction. It generally does not require complicated burner parts that may need be exposed to the high temperatures of the combustion chamber. The simple construction of the secondary fuel gas and flue gas injection tubes provides another advantageous feature. They can be positioned to accommodate most any burner configuration. The above is a brief description of some deficiencies in the prior art and advantages of the present invention. Other features, advantages and embodiments of the invention will be apparent to those skilled in the art from the following description, accompanying drawings, and appended claims. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a sectional view of a burner in accordance with the principles of the present invention; Fig. 2 is a front view of the burner of Fig. 1 in accordance with a first embodiment of the invention; Fig. 3 illustrates a further burner slot configuration of the burner of Fig. 1; Fig. 4 schematically illustrates another arrangement of the burner tubes and burner plate slots illustrated in Fig. 2; Fig. 5 is a sectional view of the burner central nozzle illustrated in Fig. 1; Fig. 6 illustrates the cone-shaped fuel jets and accompanying flame front in accordance with the present invention; Fig. 7 is a sectional view of another burner arrangement according to the present invention; and Fig. 8 is a front view of the burner of Fig. 7. DESCRIPTION OF THE PREFERRED EMBODIMENT Referring to the drawings in detail, wherein like numerals indicate like elements, burner 2 is shown in accordance with the principles of the present invention. Although the burner described below includes generally radially arranged burner slots and tubes, other nonparallel slots (or burner tube) configurations can be used, such as a triangular configuration. Referring to Fig. 1, burner 2 generally comprises housing 4 which has at one end thereof burner plate 6 through which streams of fuel gas and combustion air pass to a combustion chamber downstream therefrom. The other side of the burner housing includes a conventional door assembly (not shown) for access to the interior of the burner. Burner housing 4 is positioned within conventional wind box 8 which provides combustion air inside the burner through holes formed in the burner housing (not shown) as is conventional in the art. Wind box 8 includes mounting flanges 9 into which the burner assembly can be placed. Refractory burner throat 10 is provided around one end portion of the burner assembly to properly shape the flow of combustion products into the furnace, enhance stability, and protect the burner from the heat generated in the combustion chamber. Fuel gas supply line 12 extends through the burner and is adapted to be coupled to a fuel supply source for supplying fuel gas to manifold 14 which in turn distributes the fuel gas to burner tubes (or spuds) 16, which extend radially therefrom, and central burner 18, which is surrounded by a conventional annular air spinner 20. A conventional restrictor 22, i.e., a cylindrical wall, having through holes 24, is provided within the burner assembly to control the amount of air from the wind box that reaches the outer burner tube zone and the inner central burner zone. The restrictor forms an outer annulus and inner core of combustion air. The front face of burner plate 6 preferably is covered by refractory material 26 having a thickness of 1-1/2 inches, for example. Refractory material 26 can be applied directly to the burner plate by using wire anchors (if the plate is equipped with wire anchors on its outer face), or by premolding the refractory material and attaching it to the burner plate with nuts and bolts. The bolts and nuts can be embedded in the refractory material and a refractory plug used to close the resulting holes and protect the fasteners against excessive temperature. Referring to Fig. 2, the burner is shown in front view illustrating the preferred burner arrangement. Burner tubes 16 are illustrated as being symmetrically positioned around center axis 28 of annular burner plate 6 which has a center cut-out 29. Each burner tube 16 includes a plurality of discharge openings 30 of similar size and number which are aligned with one of the six illustrated slots 32 for directing fuel gas and air through the burner plate. The combustion recirculation zones formed between adjacent slots on the outer surface of the burner plate are generally designated with reference numeral 34. The burner tubes are supported by the manifold so that they are centered relative to the slots and spaced from the burner plate to provide fuel gas streams to flow through the slot with a certain partial mixing of fuel gas and air in the burner, as will be discussed in more detail below. Although burner plate 6 is illustrated as being annular, it can have other configurations without departing from the scope of the present invention. Fig. 3 illustrates an alternative slot configuration for the burner plate, i.e., a wedge-shaped slot 37. This configuration has the advantage of having a larger cross-sectional area toward the perimeter 38 of the burner plate, allowing more air to enter into the combustion chamber, at a given air pressure at the wind box, so that the gas flow rate can be raised to increase the burner capacity. On the other hand, if it is desired to keep the burner capacity constant, this configuration reduces wind box air pressure requirements. Fig. 4 schematically illustrates a further burner tube and slot arrangement in which the slots, as well as their corresponding burner tubes, are not equidistantly spaced about the burner plate to create a more complex flame front to reduce pulsation, as will be described in more detail below. With even slot spacing the individual flames from each slot in some instances have a tendency to "walk" from one side to the other, which might be detrimental. In the example illustrated in Fig. 4, the angle between adjacent slot centerlines 33 alternates between 50 and 70 degrees as designated with reference characters α and β, respectively. This uneven spacing is helpful in making the flow pattern more robust and stable. Referring to Figs. 1 and 2, the position of the burner tubes relative to the burner plate will be described. It is important that the fuel gas jets are aligned exactly with the burner slot centerlines (see e.g., centerline 33 in Fig. 2). Otherwise, fuel gas would be distributed unevenly across the air flow, resulting in decreased burner performance and increased NO x production. Substantial misalignment of fuel tubes or slots may cause fuel jet impingement onto the edge of burner plate 6. Such impingement can cause combustion to take place before the flow passes burner plate 6, with the result of additional flow distortion and overheating of the burner plate slot edges, which in turn could give rise to warping and flashback problems. Although the fuel supply tubes could be paced very close to the burner plate to avoid fuel gas deflection, such an arrangement would result in the mixing of fuel gas with combustion air to occur mostly downstream of plate 6 where there is high turbulence. In that case, a portion of the fuel can burn before mixing with a sufficient amount of air, resulting in increased NO x emissions. It would also cause some delay in ignition from the moment fuel gas and combustion air exit burner plate 6. This delay would require the provision of more space between the slots to ensure the requisite recirculation of hot combustion products beneath recirculation zones 34. The increased space would significantly reduce the maximum achievable flame intensity. When the ratio between the vertical distance from the burner plate slot, at a point adjacent the outer surface of the burner plate, and its respective fuel supply tube discharge opening, and the width of the burner plate slot is about 1.5:1 to 4:1, and preferably 2-3:1, high fuel velocities can be used to provide the desired combustion characteristics. The distance between radially oriented slots 32 also can influence flame intensity. When slots 32 are too close to one another, the size of the recirculation zones between slots and the residence time of the fuel gas-air mixtures when passing between recirculation zones are reduced to the extent that flame blowout results, while the load is below the desirable level. In other words, the period in which this fuel gas-air mixture remains exposed to the entraining of gases from the recirculation zones is insufficient to produce combustion and thus supply the recirculation zones with hot combustion products which sustain ignition. On the other hand, when adjacent slots are spaced too far apart, flame intensity significantly decreases with the decreasing amount of fuel and air per unit of burner cross-section, which generally is not desirable. As disclosed in U.S. Patent No. 5,102,329 with the above burner construction, very high gas flow velocities and high air velocities can be used, which in turn generates high turbulence in the combustion chamber. As a result, the flame in the combustion chamber can be a high intensity short flame. Another advantage of this construction is that with a sufficient amount of excess air, the burner generates very low NO x . This results from mixing of fuel with all of the air delivered to the combustion chamber from the burner prior to ignition, thus avoiding hot spots within the flame that are associated with combustion of mixtures close to stoichiometric proportions. Specifically, the fuel gas is first ignited at a point where it is mixed with enough excess air so that the combustion temperature does not become too high, thereby limiting the NO x production. This is done by a combination of steps: preventing an immediate ignition of the gas as it exits from the spuds by enveloping the gas with air along the distance from the spuds to the slots and, then, inducing turbulence, which is accomplished by discharging the gas and air at high speeds. As the gas stream travels downstream, it expands in a cone shape and increasingly mixes with air which flows along its margin and with recirculating hot gases. Under these conditions, ignition starts from the periphery of the cone-shaped jets discharging from the slots, and propagates by turbulent mixing to the jet centers. The local concentration of fuel on the jet periphery, where the ignition starts, is close to lean flammability limit. Additional time, required for flame propagation to the jet centers, allows averaging of fuel-air ratios on the jet centers prior to the ignition. Thus, combustion occurs downstream from the burner plate only at high local excess air conditions, limiting combustion temperature and minimizing NO x production. Low NO x burners incorporating an ignition delay as described above are known, but it has been found that the flame front generated with those systems will oscillate toward and away from the burner plate at a frequency determined by the overall construction of the burner system (for example, the frequency of the supply air flow pulsations can vary 8-200Hz). When pulsations in the heat energy release become synchronized with the supply air frequency, amplification of the flame front pulsations results, which leads to vibrations and resonance of the hardware of the furnace, known as rumbling. The undesirable vibration and resonance described above essentially do not take place in the burner of the present invention because of the arrangement of the burner tubes and slots which, as described in more detail below, affect the configuration of the recirculation zones so that local oscillations of flame front occur at different frequencies and are not synchronized, so that vibrations are greatly dampened and resonance problems essentially do not occur. Returning to Fig. 2, the burner is illustrated as having six radially extending and equidistantly spaced burner tubes or spuds 16 (i.e., each burner tube pair forms an angle of about 60°). The distance between the outer end portions of adjacent burner slots is substantially greater than the distance between the inner end portions of the adjacent slots. Since the burner tubes are aligned with the slots, they are similarly arranged. This configuration results in a substantial tapering of the recirculation zone 34 in the direction of the central region of the burner plate. Preferably the ratio between the distance between the outer end portions of adjacent burner slots (or tubes) and the distance between the inner end portions is at least about 2.5:1 to provide sufficient change in the recirculation zone from the central portion of the burner plate to the perimeter of the burner plate so that ignition of adjacent flame fronts will not be synchronized. Although the burner is illustrated with six burner tubes, other multiples of burner tubes can be used within the scope of the invention. In addition, other slot and burner tube configurations can be used in which the width or area of the recirculation zones varies significantly between the burner plate center axis 28 so that the local ignition patterns vary such that local oscillations of flame front occur at different frequencies and are not synchronized. For example, the slots can be arranged in a nonparallel configuration such as a triangle. As discussed above, the slots and burner spuds also can be asymmetrically arranged about burner center axis 28 or arranged such that the burner spuds are not equidistantly spaced about the burner plate, to form a more complex flame front and minimize pulse synchronization. An example is illustrated in Fig. 4 where the angle between adjacent burner slots (or spuds) alternates between 50° and 70° as designated by reference characters a and β. Burner plate 6 includes a central cut or opening 29 where central burner nozzle 18 and spinner 20 are arranged. Preferably, opening 29, nozzle 18, and spinner 20 are concentrically positioned about burner center axis 28. Central nozzle 18 and spinner 20 add to the complexity of the flame front shape and further render the burner less sensitive to pulsating supply air, minimizing rumbling. A central burner nozzle 18 provided with a plurality of tangentially drilled gas discharge ports 42 (shown in Figs. 1 and 5) induces a swirl in the center of the combustion chamber and in tests has functioned exceedingly well. However, it is believed that other nozzle designs, including a different arrangement of discharge ports than illustrated in Fig. 5, should work equally well. It also has been found that when the burner spud arrangement described above is used in combination with central burner nozzle 18, that enhanced flame stability results. That is, flame blow-out is not a concern up to about 110% excess air. One advantage of this relatively wide range, is that it reduces the requirements of the control system to control the fuel-to-air ratio since the ratio is less critical in view of the relatively wide range noted above. The operation of the burner will be described with reference to Fig. 6. Fuel gas, at a pressure of about 10 psig in fuel gas burner tubes 16, is discharged at a very high speed through fuel gas tube discharge openings 30, i.e., at full load the fuel gas exits the spuds at 200-400 m/s in the direction of the slots in plate 6. Combustion air, generally designated with reference numeral 46, flows through the burner slots also at a velocity of about 30-40 m/s. The very high fuel gas and combustion air velocities generate very high turbulence in the combustion chamber so that the desired high intensity flame is achieved, while the ignition of the fuel is delayed to a point downstream from the burner plate where it has been mixed with enough excess air so that the combustion temperature does not become too high thereby limiting NO x production. As the cone-shaped fuel gas jet 44 expands downstream, air progressively frays at its margin. A flame front 47 is established at a point downstream from the burner plate where sufficient amount of recirculating hot gases penetrate into the cone-shaped jet for ignition. As shown in Fig. 6, the resultant flame is anchored to burner plate refractory 26. The marginal eddy currents of the recirculation gases in the recirculation zone are generally indicated with reference numeral 48. Since the width of the recirculation zones varies significantly with the distance from the center axis 28 of the burner plate, the local ignition patterns also vary. As a result, local oscillations of flame front occur at different frequencies and are not synchronized. In this way, vibrations are greatly dampened and resonance problems are minimized or eliminated. Merely to exemplify the makeup of a burner that was tested and provided the foregoing results, the following example is recited. This example is given for purposes of illustration, and is not intended to limit the scope of this invention. The outside diameter of the burner plate was 20 inches and the center hole in which the central burner nozzle and spinner were arranged had a diameter of 8 inches. Six radial slots and burner tubes were arranged around the central burner nozzle and spinner as illustrated in Fig. 2. The slot widths were about 2 inches, while the distance between the discharge openings of each burner and the outermost point of the corresponding burner plate slot was about 4 inches. Air flow was provided through the radial slots and the annular spinner at a ratio of 98:2. The center burner nozzle was operated close to stoichiometric conditions, while the radial slots ran with 70-110% excess air. These parameters are especially appropriate for air heaters. For boiler applications where high amounts of excess air can greatly reduce the efficiency of the boiler system, the total amount of excess air can be reduced by means of secondary fuel injection. A further embodiment of the present invention including a secondary fuel injection system is shown in Figs. 7 and 8. Referring to Fig. 7, two-stage burner assembly 2' essentially differs from burner 2 in that burner assembly 2' includes a secondary fuel gas assembly for generating a two-stage combustion flame. In addition, central or core burner 50 is preferably substituted for central burner 18 and spinner 20 and restrictor 22 are eliminated. Central or core burner 50 comprises a hollow tube or cylinder 52 and baffles 54 and 56. Each baffle 54 and 56 is preferably annular, i.e., ring shaped, and concentrically positioned within tube or cylinder 52 by support member 58, which preferably is cylindrical and has at least one closed end to prevent fuel gas flow therethrough. Fuel gas is supplied to the interior of cylinder 52 via fuel gas supply line 12' which extends through end wall 59 of burner 50 is adapted to be coupled to a fuel supply source (not shown). The fuel gas, generally designated with reference arrows 60, flows downstream and enters ports 62 which are formed in baffle 54. Although hidden in this view, ports 62 are provided 360° around baffle 54. As the fuel gas exits ports 62, baffle 56 induces turbulence in the fuel gas stream which then passes over baffle 56 and mixes with combustion air passing through circumferentially spaced holes 66 formed through cylinder 52. The fuel gas and combustion air mixture is discharged from the downstream open end of cylinder 52 and ignited to form a standing pilot for the primary fuel gas and combustion air mixture which will be discussed in more detail below. Central burner 50 is positioned within burner housing 4'. Burner housing 4' is generally cylindrical and positioned within conventional wind box 8' which supplies combustion air to burner housing 4' by way of holes 68 that are formed in the burner housing as is conventional in the art. Wind box 8' further includes air inlet conduit 70 for supplying pressurized air within the wind box as is conventional in the art. Thus, inlet conduit 70 can include a conventional damper (not shown) for regulating air flow rate. The pressurized air flows through housing 4' and exits via pilot holes 66 and burner plate slots 32. Burner assembly 2' is shown coupled to a boiler of which boiler plate 71 forms an end wall thereof as is conventional in the art. In this example, one end of housing 4' preferably is secured to boiler plate 71. The connection can be made with fasteners or by welding, for example. The other end of housing 4' opposite burner plate 6 includes a conventional door assembly (not shown) for access to the interior of the housing. In the preferred embodiment, any one of the burner plate and spud configurations described with reference to Figs. 1-6 forms the primary combustion air and fuel gas discharge assembly. However, for purposes of simplification, burner assembly 2' will be described in conjunction with the burner spud arrangement shown in Fig. 2. As in Fig. 2, burner plate 6 includes a center cut-out 29 for receiving the central or core burner. However, cut-out 29 is sized in burner assembly 2' to accommodate tube or cylinder 52 which extends through the center portion of the burner plate and provides a support therefor. The fuel gas feed system for burner tubes 16 also is slightly modified to accommodate the configuration of central burner 50. Specifically, fuel gas is supplied to burner tubes 16 by way of annular manifold 72 which is fluidly coupled to the outer end portions of the tubes. Manifold 72 also serves as a support for tubes 16 so that they are centered relative to the slots 32 and spaced from burner plate 6 as described above with reference to Figs. 1 and 2. Referring to Fig. 7, burner assembly 2' is provided with secondary fuel gas discharge assembly 80. Assembly 80 generally comprises a plurality of secondary fuel gas injection tubes 82 circumferentially spaced about burner plate 6 and extending through refractory burner throat 10. Each secondary fuel gas injection tube 82 is fluidly coupled to annular manifold 84. Manifolds 84 and 72 (discussed above) are connected, by conventional control valves, to pressurized fuel gas source supply 86, which is diagrammatically shown in Fig. 7. Although separate manifolds 72 and 84 are shown, which is preferred for very high turn down, a single manifold can be used to distribute fuel gas to the primary and secondary fuel gas assemblies. Fuel gas source 86 also is fluidly coupled to line 12' via a regulator (not shown) as is conventional in the art. Referring to Figs. 7 and 8, the discharge end of each injector 82 includes a nozzle 88 having discharge ports 90 (Fig. 8) oriented for directing the fuel gas toward centerline 28 of the burner plate 6 as shown with reference arrow 92 (Fig. 7). Secondary fuel gas discharge assembly 80 also includes a plurality of recirculation flue gas injection tubes 94 which also are circumferentially spaced about burner plate 6 and extend through burner throat 10 for injecting recirculated flue gas into the combustion flame downstream from burner plate 6. Each recirculation flue gas injection tube is fluidly coupled to annular manifold 96 which, in turn, is fluidly coupled to a conventional flue gas stack 98 (diagrammatically shown) by way of flue gas line 100. The flue gas stack coupled to the boiler as is conventional in the art. Flue gas line 100 includes a fan 99 (diagrammatically shown) to draw flue gases from stack 98 and inject those flue gases through injectors 94 in a forced draft. The other end of each recirculation flue gas injection tube includes a nozzle 102 having a plurality of discharge ports 104 (Fig. 8) which are oriented for discharging the flue gas stream toward centerline 28 of burner plate 6 as designated with reference numeral 106 (Fig. 7). By angling the gas stream discharged from nozzles 88 and 102 toward the centerline of burner plate 6, but sufficiently downstream into the combustion chamber, two combustion zones can be generated. For example, when using 15% excess air (e.g., about 3% in excess of stoichiometric concentration of oxygen) with the primary air and fuel gas discharge assembly, some of the air is not consumed in the first combustion zone where lean combustion takes place. By angling the recirculation flue gases and secondary fuel gas toward the centerline of burner plate 6, they mix with the combustion air entering through burner plate slots 32 so that the fuel gas from nozzle 88 combusts some distance downstream of the burner plate, i.e., in a secondary combustion zone. By not supplying the secondary fuel gas with air, but instead, with flue gas (which contains very little, e.g., 3%, oxygen), combustion is delayed and the volume of nonreacting gases downstream of the burner is increased. The resulting delay in the combustion of the gas from nozzle 88 and the need for heating the added flue gas lowers the overall combustion temperature in the second zone, which in turn reduces the generation of NO x . In the preferred embodiment, each secondary fuel gas injection tube 82 is concentrically positioned within one of the recirculation flue gas injection tubes 94 to provide optimal performance. However, the secondary fuel gas tubes can be positioned outside the flue gas tubes, provided that each fuel gas and flue gas tube pair is oriented so that their discharge nozzles are in the vicinity of one another. The fuel and flue gas injection tube pairs also preferably are positioned midway between adjacent slots 32 to provide optimal performance with respect to low emissions and low vibration in low excess air applications. Thus, six fuel and flue gas pairs preferably are used in connection with a primary fuel and air discharge assembly having six radially extending burner slots as illustrated in Fig. 8. It is also noted that the orientation of secondary fuel gas discharge assembly 80 can differ from that in Fig. 7. For example, the fuel and flue gas tubes 82 and 94 can be angled radially inward to form an angle (e.g., 15°) with centerline 28 of burner plate 26 that is sufficient to have the flue and secondary fuel gases enter into the secondary combustion zone as discussed above. Thus, this angle depends on the particular burner dimensions. It also should be understood that the secondary fuel gas discharge assembly 80 can be positioned outside wind box 8'. Burner assembly 2' also can be readily modified for use with fuel oil as opposed to fuel gas. In this case, support member 58 is dimensioned to extend the length of housing 4' to support a conventional oil gun therein. Accordingly, the support member would be hollow and open at both ends. For purposes of illustration, oil gun 107 is shown in phantom in Fig. 7. When the oil gun is used, all fuel gas supply lines are closed, but the recirculation flue gas lines are open. The fuel oil from the oil gun would be combusted in the primary combustion zone with combustion air entering the combustion chamber through burner slots 32. The recirculation flue gas enters the secondary combustion zone in the combustion chamber via flue gas nozzles 102 to lower the overall temperature of the flame as discussed above. In order to provide a dual fuel system (oil or gas), combustion air inlet ports can be provided in flue gas injection tubes 94 together with a mechanism for opening or closing those ports depending on the requirements of the application. Generally, the ports are closed on gas firing and opened on oil firing. That is, flue gas injection tubes 94 can be provided with inlet ports (not shown) for receiving combustion air from wind box 8' to provide additional combustion air to the secondary combustion zone to reduce NO x on oil firing. This configuration also simplifies controls by making the draft loss coefficient for the burner for gas and oil. about the same.

Claims: A burner comprising: an annular burner plate (6) having an outer surface for facing a combustion chamber, an inner surface, and a plurality of circumferentially arranged radially extending slots (32) formed therethrough for introducing air and fuel gas into a combustion chamber, and a radially extending burner tube (16) provided for each of said slots (32) each tube (16) having an inner end portion adapted to be coupled to a fuel gas source, an outer end portion, and a plurality of discharge openings (30) for directing fuel gas through its associated slot (32) into said combustion chamber, the distance between the outer end portions of adjacent burner tubes (16) being substantially greater than the distance between the inner end portions of said adjacent tubes (16). The burner of claim 1, characterized in that the ratio between said distance between the outer end portions and said distance between the inner end portions is at least about 2:1. The burner of claim 1, characterized in that means for discharging combustion air from said slots (32) are provided. The burner of claim 1, characterized in that the width of each slot (32) increases as the slot approaches the outer perimeter of said burner plate (6). The burner of claim 1, characterized in that said recirculation zones (34) are larger in area than said slots (32) . The burner of claim 1, characterized in that a plurality of discrete flue gas injection tubes (94) are provided, each having a discharge end portion (104) that is positioned radially outward from an imaginary cylinder extending normal to and surrounding said plurality of circumferentially arranged slots (32), each flue gas injection tube (94) having an inlet adapted for coupling to a flue gas recirculation line (100) adapted for coupling to said combustion chamber; and a plurality of secondary fuel injection tubes (82) adapted to be coupled to a fuel gas source (86), each having a discharge end portion (90) adjacent said discharge end portion (104) of one of the flue injection tubes (94). The burner of claim 6, characterized in that the discharge end portion (90) of each secondary fuel gas injection tube (82) is substantially concentrically positioned within said discharge end portion (104) of one of the flue gas injection tubes (94). The burner assembly of claim 1, characterized by multiple fuel and flue gas tubes, each having a discharge end portion that is spaced radially outward from said burner plate slots (32) of the primary discharge assembly, a first group of said tubes (82) adapted for coupling to a fuel gas source (86) and a second group of said tubes (94) adapted for coupling to a flue gas source (98), each of said tubes including a nozzle (102) having an outlet arranged for directing gas discharged therefrom toward the center axis (28) of the primary discharge assembly. The burner assembly of claim 8, characterized in that the discharge end portion (90) of each tube (82) from said first group is substantially concentrically positioned within the discharge end portion (104) of one of the tubes (94) from the second group. The burner assembly of claim 8, characterized in that said flue gas source includes a flue gas stack (98) downstream from and in fluid communication with said combustion chamber; each of said second group of tubes (94) has a discharge end portion (104) that is spaced radially outward from said primary air and fuel gas discharge assembly; a flue gas recirculation line (100) has one portion fluidly coupled to said flue gas stack (98) and another portion fluidly coupled to inlets of said second group of tubes (94); and a flue gas recirculation line (100) has one portion fluidly coupled to said flue gas stack (98) and another portion fluidly coupled to inlets of said second group of tubes (94); and a fan (99) is coupled to said flue gas recirculation line (100) so that a forced draft of recirculated flue gases can be directed through said flue gas injection tubes (94) and into a particular region of said flame.

Inventors: LIFSHITS VLADIMIR, LONDERVILLE STEVE B, LIFSHITS, VLADIMIR, LONDERVILLE, STEVE B.
Applicants: COEN CO, COEN COMPANY, INC.
Application year: 1994
Main classification: F23D14
IPC codes: F23C6, F23D14, F23C9